KR102370023B1 - hydrodynamic coupling - Google Patents

Abstract

The fill-controlled hydrodynamic coupling includes a pump wheel and a turbine wheel defining a working space and capable of being mechanically connected to one another by a hydraulic fluid; direct circulation connecting the hydraulic outlet of the working space with the hydraulic inlet; a pumping device hydraulically disposed between the fluid source and the direct circulation; and a lubrication line from the pumping device to the lubrication point of the coupling. wherein the pumping device is designed to deliver a fluid from the fluid source into the working space and into the lubrication line in a first delivery direction or from the working space to the fluid source in a second delivery direction.

Description

hydrodynamic coupling

The present invention relates to hydrodynamic couplings, also referred to as flow couplings or turbocouplings. More particularly, the present invention relates to a charge controlled hydrodynamic coupling with direct circulation.

The hydrodynamic coupling is designed to transmit torque between the input side and the output side. The input side is connected to a pump wheel and the output side is connected to a turbine wheel, the wheels defining a working space. When the working space is filled with a fluid, it causes a hydrodynamic coupling between the rotational movements of the input side and the output side. In fill-controlled couplings, the degree of coupling may be affected by the amount of fluid present in the working space. A fill pump is typically provided for delivering a fluid into the working space. Part of the delivered fluid is divided and guided to lubrication points, in particular to rotating bearings mounted on the pump wheel or the turbine wheel. A direct circulation connecting the hydraulic outlet of the working space with the hydraulic inlet is often provided. The outlet is usually provided radially on the outside of the pump wheel so that the fluid is conveyed through the outlet under the influence of centrifugal force according to the principle of a dynamic pump. The inlet is preferably provided more radially on the inside to ensure the necessary pressure gradient for circulation of the fluid. Often a heat exchanger is provided in the direct circulation to cool the circulating fluid.

In the case of semi-open direct circulation, the working space has a more permanently open outlet for the fluid through which the fluid flows during operation of the coupling. Fluid flowing outward and dripping from the lubrication points is collected in a tank to which the fill pump is supplied. The filling pump must always be operated to maintain the filling of the working space in the case of the semi-open circuit since a fraction of the delivered quantity is required to supply fluid to the lubrication points. An undesired delivery amount is typically provided back into the tank by a bypass valve. In order to empty the hydrodynamic coupling, a controllable discharge valve is often provided in the working space. However, the discharge valve and its operation can be complicated and can reduce the usefulness or durability of the coupling.

An Italian company, Transfluid, has proposed a fill-controlled hydrodynamic coupling installation with a pump in which the delivery amount can be varied to fill the working space with a fluid. By obstructing the flow of oil into the coupling, the working circuit is emptied and the drive input is disconnected from the drive output. This disconnection may be facilitated by a quick release valve. This solution requires providing a separate lubrication oil pump to supply fluid to the lubrication points. To control the drive torque or the rotational speed of the pump, the configuration for use can consist of a frequency converter motor denominated Danfoss VLT Drive Motor FCM 106.

The object of the present invention is based on the specification of a technique which makes it possible to construct or operate a fill-controlled hydrodynamic coupling in a simplified manner. This object of the invention is realized by the subject matter of the independent claims. Preferred embodiments are provided in the dependent claims.

The fill-controlled hydrodynamic coupling defines a working space and includes a pump wheel and a turbine wheel that can be mechanically coupled to each other in a hydraulic fluid. The coupling comprises a direct circulation connecting the hydraulic outlet of the working space with the hydraulic inlet; a pumping device hydraulically disposed between the fluid source and the direct circulation; and a lubrication line connected from the pumping device to the lubrication point of the coupling. wherein the pumping device is designed to deliver a fluid from the fluid source into the working space and into the lubrication line in a first delivery direction or from the working space to the fluid source in a second delivery direction.

Said coupling means that additional lubricating oil pumps can be provided together, but advantageously only one pump can be operated. To reduce the amount of fluid located within the working space, the pump may be operated in the second delivery direction, so that a controllable quick-emptying valve in the working space may not be required. . Additional valves may be provided to control the fluid balance of the coupling. The coupling can thus be configured in a simpler and more reliable manner of operation.

More preferably, the pumping device is designed to vary the amount of the delivered volumetric flow rate. For this purpose, in particular an electric motor can be provided to drive the pumping device, which can be controlled in terms of direction of rotation and speed or torque of rotation, for example by means of a frequency converter. In order to fill the working space with the fluid, the pumping device can be operated at a high volumetric flow rate in the first delivery direction. To this end, the drive electric motor can be operated up to maximum power. When the drive motor comprises an electrically asynchronous machine, the machine can be operated above and beyond its nominal rotational frequency within the field-weakening range to achieve the high volumetric flow rate. Use can be made with a relatively small electric motor to drive the pumping device, nevertheless it is possible to ensure that the working space can be quickly immersed with fluid.

When a desired amount of fluid is located within the working space, the pumping device may be operated at a reduced volumetric flow rate in the first delivery direction. To this end, the pumping device or the electric motor is controlled such that exactly the same fluid is delivered into the working space as it leaves the working space. When no fluid escapes from the working space, the pump may also be turned off. Here, the volumetric flow rate flowing through the pumping device may preferably be greater than the amount required to supply fluid to the lubrication points. If operation of the pump to supply the working space is not required, the pump may be operated to supply the lubrication points. To this end, a periodic operation of the pump may also be provided. In order to deliver the low volumetric flow rate, the pumping device or the electric motor driving it is typically operated with reduced power. Compared to conventional solutions having a bypass valve and a pumping device operated at a constant volumetric flow rate, a substantial amount of energy can be saved. It is also possible to avoid situations in which large fluid volumes are permanently circulated by the pumping device.

It is further preferred that a tank is provided as a fluid source, wherein the fluid exiting the working space or from the lubrication point is directed into the tank. In a fill controlled hydrodynamic coupling with direct circulation, the size of the tank is determined by the delivered volumetric flow rate of the pumping device and the residence time of the fluid in the tank in addition to the circuit volume to be accommodated at rest. For a given residence time, the volume received in the tank will therefore depend largely on the volumetric flow rate of the pumping device. When the pumping device is operated with a small volumetric flow rate during normal operation of the coupling as described above, the volume of the tank can be substantially reduced compared to conventional solutions. The tank can be reduced to a fluid volume of 1.2 to 1.5 times for full fill. For an intended cycle time of 2 minutes or less, a tank volume of 1.1 times the maximum filling volume of the working space may be sufficient. Said reduced tank can be arranged at an advantageous point in a simpler way. The coupling can be designed to be integrated with the tank, and due to its smaller overall volume it is possible for the coupling to be used in an improved way even under limited space conditions.

The possibility of a reduced volumetric flow rate of the pumping device during operation of the coupling means that the lines or valves of the coupling can be of a smaller design or can be arranged, which can result in cost savings. If an electrically controllable valve is provided in the hydraulic system of the coupling, a clocked operation may not be required to effectuate only a partial opening of the valve on average over time. The life of the valve may be increased accordingly, or a valve may be provided for varying the torque transmitted through the coupling.

More preferably, the working space further comprises a permanently open outlet for the fluid. This outlet may include one or more nozzle bores in particular in the radially outer region of the pump wheel. Such a design may be referred to as a half-open circuit. The exchange of fluid between the fluid source and the working space can be increased accordingly, resulting in that heat dissipation can be improved or the load of the fluid can be reduced. In addition, the working space may be gradually emptied when the power to the pumping device is turned off.

In another embodiment, a controllable drain valve is provided for draining a fluid from the working space. Such a discharge valve may maintain the Lenz effect of the pumping device. The discharge valve may be configured as, for example, a hydraulically controlled membrane valve.

More preferably, a heat exchanger is arranged in the direct circulation, wherein the pumping device is hydraulically connected to the direct circulation between the heat exchanger and the inlet of the working space. For the direction of circulation of the fluid in the direct circulation, the pumping device is thus connected downstream of the heat exchanger. In particular, when the coupling is stationary, the pumping device is operable in the first delivery direction to deliver a fluid through the heat exchanger as opposed to a normal flow direction. Static cooling can thus be implemented to cool the fluid of the coupling even when the pump wheel of the coupling is stationary. It is also possible to arrange such a configuration together with the previously mentioned controllable discharge valve. Moreover, the heat exchanger can be heated by the pumping device to achieve a faster or smoother operating temperature of the heat exchanger, for example at low external temperatures.

In another embodiment, a heat exchanger is arranged in the direct circulation, wherein the pumping device is hydraulically connected to the direct circulation between the fluid source and the heat exchanger, wherein a controllable discharge valve is in the region of the inlet. in the direct circulation phase. In this embodiment, static cooling may be controlled through the normal flow direction of the heat exchanger. The pumping device delivers a fluid into the heat exchanger from which the fluid can be discharged directly back without passage into the working space.

The coupling system includes the coupling described above in any desired embodiment and a control device for controlling the pumping device. The pumping device may be controlled in different ways with respect to its delivery direction and/or its volumetric flow rate. In a particularly preferred embodiment, the pumping device is driven by an electric motor, in particular a three-phase asynchronous machine, the control device being designed to control the direction of rotation and/or the speed of rotation of the electric motor. To this end, use can in particular consist of field-oriented open-loop control or field-oriented closed-loop control. The control device preferably comprises a programmable microcomputer or microcontroller for performing the control task. It is further preferred that the control device has an interface for controlling the parameters to be received.

It is more preferred that the coupling has at least one sensor mounted thereon, for example a rotation speed sensor or torque sensor on the turbine wheel, a pressure sensor or temperature sensor on one of the hydraulic lines, or a different or additional sensor. and the at least one sensor is connected to the control device. The control device can in particular be designed to fully control the coupling, ie to achieve complete fluid control, eg depending on the requirements of the torque transmitted, the slip maintained or the rotational speed observed. For example, filling of the working space depending on predetermined initiating characteristics and maintenance of a fluid level in the working space or emptying of the working space according to other predetermined characteristics may be controlled by the control device. In addition, cooling of the fluid by an optional heat exchanger or heating of the heat exchanger at very low external temperatures can be controlled.

It is particularly preferred if the control device is arranged in the region of the coupling. The control device can be designed to control the coupling in a certain way, with the result that the risk of using undesirable parameters or characteristics can be reduced. In addition, the cost in terms of connecting or wiring the coupling and the control device in the positional use of the coupling can be greatly reduced. Thus, a stable and accurate behavior of the hydrodynamic coupling can be ensured under all operating conditions independently of external control requirements. The coupling can be operated in place more quickly and more reliably. The interface through which control requests from external logic can be received can be simplified.

In another embodiment of the coupling system, a heat exchanger is arranged in the direct circulation, wherein the coupling comprises a fan for evacuating the heat exchanger, and the control device is designed for controlling the fan. The heat exchanger and the fan may be integrated into the coupling system or may be provided separately.

The fill-controlled hydrodynamic coupling includes a pump wheel and a turbine wheel defining a working space and capable of being mechanically connected to one another by a hydraulic fluid; direct circulation connecting the hydraulic outlet of the working space to the hydraulic inlet of the working space; a pumping device hydraulically disposed between the fluid source and the direct circulation; and a lubrication line connected from the pumping device to the lubrication point of the coupling. The method for controlling the fill-controlled hydrodynamic coupling comprises: operating the pumping device in a first delivery direction to supply fluid to the lubrication point and the working space; and operating the pumping device in a second delivery direction to reduce the amount of the fluid received within the working space.

In other embodiments, the pumping device maintains a high volumetric flow rate in the first delivery direction to increase the amount of the fluid received within the working space, or constant the amount of the fluid received within the working space. It is preferable to operate at a low volumetric flow rate for this purpose. The high volumetric flow rate is greater than the low volumetric flow rate. To deliver the high volumetric flow rate, the pumping device can be operated at maximum drive power, with the result that the high volumetric flow rate corresponds to or approximates the maximum deliverable volume flow rate. The low volumetric flow rate is preferably as low as possible to correspond in quantitative terms to the sum of the leakage of the fluid from the working space and the volumetric flow rate of the fluid flowing through the lubrication points. In other words, the low volumetric flow rate is realized when the amount of fluid contained within the working space remains the same.

How much fluid is intended to be present in the working space may depend, inter alia, on the torque transmitted, the rotational speed achieved and the demand for slip entrained between the pump wheel and the turbine wheel.

In yet another embodiment, the pumping device is pulsed in the first delivery direction to supply fluid to the lubrication point while the slip between the pump wheel and the turbine wheel is about 100%. A permanent operation of the coupling can thus also be ensured even in the case of extremely high slip rates without compromising the supply of fluid to the lubrication point. 100% slip is typically achieved when the input side connected to the pump wheel is rotating while the output side connected to the turbine wheel is substantially stationary. When the coupling is filled only with gaseous medium, some fluid is introduced into the working space and removed again in a pulsed manner to eliminate the resulting exhaust heating.

The method described above may be implemented with program code means on a processing device or as a computer program product stored on a computer readable data carrier. The processing device may be included in or may be the same as the aforementioned control device. The processing device preferably includes a programmable microcomputer or microcontroller.

The features of the method described above relate directly to the apparatus described above, so that features mentioned in relation to one of the two categories may also be applied to the other category in a subsequent manner.

Hereinafter, the present invention will be described in more detail with reference to the accompanying drawings, in which
1 shows a schematic illustration of a coupling system,
2 shows a hydraulic circuit diagram of a coupling system in another embodiment;
3 shows diagrams of an exemplary embodiment of a coupling system;
4 shows a block diagram of a coupling system;
5 shows a flow diagram of a method for controlling coupling of a coupling system.

1 shows a schematic illustration of a coupling system 100 having a fill-controlled hydrodynamic coupling 105 . The coupling 105 is designed for controllable transmission of rotational motion between the input side 110 and the output side 115 which are mounted rotatably with respect to each other about a common axis of rotation 120 . The coupling 105 includes a pump wheel 125 connected to the input side 110 and a turbine wheel 130 connected to the output side 115 . The pump wheel 125 is a working space in which a fluid 140 together with the turbine wheel 130 can be accommodated to hydrodynamically connect the turbine wheel 130 with the pump wheel 125 . (135) is formed. Here, the degree of coupling depends on the amount of fluid 140 accommodated in the working space 135 . The pump wheel 125 and the turbine wheel 130 are typically rotatably mounted by bearings 145 . A lubricating line 150 is provided to supply a fluid 140 to the bearings 145 . The fluid 140 may include an aqueous or oily liquid.

An outlet 152 hydraulically coupled by direct circulation 154 to an inlet 156 located more radially inwardly from the working space 135 within a radially outer region of the working space 135 . is provided In a known manner, a dynamic pressure pump is preferably formed in the region of the outlet 152 in which a collection channel for the fluid 140 is provided radially on the outside of the pump wheel 125, the A collection pipe connected to the outlet 152 is immersed in the fluid 140 accumulating in the channel under the action of centrifugal force.

One or more outlets 158 are also preferably provided in the working space 135 , which are permanently open to drain the fluid 140 from the working space 135 . Fluid 140 exiting the working space 135 or from one of the bearings 145 is preferably collected and directed into a tank 160 serving as a fluid source. The tank 160 may be disposed below the working space 135 or at another point. Where appropriate, a pump in the bottle is required to deliver the captured fluid 140 into the tank 160 according to the dry sump principle.

In addition to the coupling 105 , the coupling system 100 includes a hydraulic system 162 , a pumping device 164 and a control device 166 . The control device 166 preferably comprises an interface 168 for communication with external devices, in particular the delivery direction of the pumping device 164 and preferably the volume of the pumping device 164 . It is also designed to control volumetric flow. To this end, the pumping device 164 preferably comprises a pump and an electric motor, wherein the control mechanism 166 is capable of controlling the electric motor in terms of the direction and speed of its rotation.

In the illustrated embodiment, the pumping device 164 is hydraulically connected to the tank 160 on one side and connected to both the lubrication line 150 and the inlet 156 on the other side. In a first delivery direction, the pumping device 164 delivers a fluid 140 from the tank 160 into the lubrication line 150 and the inlet 156 .

In the illustrated embodiment, the direct circulation 154 extends through a heat exchanger 170 which may preferably be actively evacuated by a fan 172 . The fan 172 may be controlled by the control device 166 . A bypass valve 174 and/or an orifice plate 176 may be connected in parallel to the heat exchanger 170 . Without the influence of the pumping device 164 , in the example of FIG. 1 , the flow passes from bottom to top through the heat exchanger 170 in the direct circulation 154 . The second connection of the pumping device 164 is connected in the region of the direct circulation 154 located between the heat exchanger 170 and the inlet 156 . A nonreturn valve 178 enables the flow of fluid 140 from this area to the pumping device 164 . The bypass valve 180 may enable flow in the opposite direction. The discharge pressure of the bypass valve is about 1.5 bar. This bypass valve is intended for supply of sufficient lubricant pressure. Another bypass valve 182 may optionally be provided from this point to the inlet 156 , which may be connected in parallel with the orifice plate 184 to enable a continuous standby operation. The discharge pressure of the bypass valve 182 may be about 0.7 bar.

A second side of the pumping device 164 is also connected to the lubrication line 150 , in which a filter 188 together with a non-return valve 186 and preferably optionally a parallel connected bypass valve 190 is provided. It may be placed within such a connection.

For improved control, one or more temperature sensors 192 and/or one or more pressure sensors 194 may be disposed at different points in the hydraulic system 162 . The sensors 192 and 194 may be connected to the control device 166 . Other possible sensors may include a rotation speed sensor on the output side 115 , an oil level sensor or a clogging sensor on the filter 188 .

To further explain the mode of operation of the coupling system 100 , by way of example, the input side 110 rotates at a constant speed, whereas initially the fluid 140 is not located in the working space 135 , It is assumed that the output side 115 is stopped. To create a mechanical coupling between the output side 115 and the input side 110 , the pumping device 164 transfers the fluid 140 from the tank 160 in the first delivery direction to the inlet 156 . is operated to pass along the direction of Here, the pumping device 164 is controlled to the maximum possible available volumetric flow rate to enable rapid filling of the working space 135 . A portion of the fluid 104 delivered by the pumping device 164 is guided to the lubrication line 150 , thereby filling the bearings 145 with the fluid 140 during the filling operation of the working space 135 . is guaranteed to be supplied.

When the working space 135 is charged, the input side 110 and the output side 115 rotate at similar rotational speeds after a specific starting time. The pumping device 164 is then preferably operated with a reduced volumetric flow rate of this size precisely to which the fluid 140 exiting through the lubrication line 150 and, where appropriate, through another outlet 158 is refilled. can be

When the coupling between the input side 110 and the output side 115 is canceled, the pumping device 164 directs the fluid 140 from the direct circulation 154 to the tank 160 in a second delivery direction. is operated to pass it back into Power transmission between the input side 110 and the output side 115 is thus canceled. Here, a large volumetric flow is again caused to disconnect the coupling 105 preferably as quickly as possible.

When the coupling 105 has to be operated for a relatively long time with a slip of about 100%, for example, when the input side 110 is driven and the output side 115 is stopped, the pumping device 164 is operated in a pulsed manner in the first delivery direction. With each pulse, fluid 140 is introduced into the lubrication line 150 , where the selected fluid level in the working space 135 can be held constant, on average, over time. In order to maintain the partial fill, it is required that the pump is then operated like a pulse in the second delivery direction to also remove the fluid again from the working space. This mode of operation having a pulse operation in the first and second transfer directions may also be provided with a relatively low slip rate. High slip values can thus be maintained at any desired fill levels of the coupling 105 for any desired time interval.

2 shows a hydraulic circuit diagram of the coupling system 100 corresponding to the case of FIG. 1 in another embodiment. Elements indicated by a cross mark in a circle may be distributed in certain embodiments. Alternatively, the elements and features shown may continue corresponding to the embodiment illustrated in the drawings, or vice versa.

By way of example, the coupling 105 is received in a housing 202 on which a ventilating means 204 may be provided. A heating device 206 , in particular a heating bar, a temperature sensor 192 and/or a level switch 208 , can be mounted in the region of the tank 160 . An inspection glass 210 may also be mounted to monitor the fluid level. Orifice plates 212 can in each case be arranged between the lubrication line 150 and the bearings 145 .

1 in that the illustrated embodiment is connected to the direct circulation 154 in the region between the outlet 152 and the heat exchanger 170 instead of between the heat exchanger 170 and the inlet 156 . substantially different from the embodiment of A further line is connected from the point between the check valve 186 and the filter 188 to the inlet 156 , particularly preferably downstream of the check valve 186 . Orifice plate 214 is inserted into this line. Also, a controllable 2/2-way valve 216 is preferably provided between the direct circulation 154 and the tank 160 . When the valve 216 is opened, there is a direct fluid connection between the tank 160 and the downstream side of the heat exchanger 170 . One or two bypass valves 218 are provided to prevent the heat exchanger 170 from emptying into the tank when the heat exchanger 170 is placed above the maximum oil level in the tank.

A torque sensor 220 and/or a rotation speed sensor 222 may be mounted on the output side 115 .

3 shows an exemplary embodiment of a coupling system 100 . The illustrated form is known under the designation Turbo Belt 500 and is based on the VTK 492 DTPXLKL type. Here, VTK denotes a voice turbocoupling, 492 denotes an outer diameter in mm, and D denotes two pump wheels 125 and two turbine wheels 130 respectively connected in parallel (the above denotes the point where the pump wheels lie axially between the turbine wheels), TP denotes the charge control coupling 105 and XL denotes the use of a specially formed space 135 with increased volume, independently mounted KL with inlet and outlet sides indicates that the tank 160 , hydraulic valves and an active coupling system together with TP are provided on the coupling 105 . The coupling 105 may be usefully used, for example, to drive a belt conveyor.

The isometric view of the coupling 105 is shown from the left in the left area of FIG. 3 and the other views are shown from the right in the right area. Here, the pumping device 164 and the control device 166 are mounted on the left side of the coupling system 100 , in another embodiment these elements may also be provided on the opposite right side. there is. The control device 166 is preferably mounted in the region of the coupling system 100 or the coupling 105 . In particular, the control device 166 may be mounted directly on the pumping device 164 or on an electric motor driving the pumping device. Although the heat exchanger 170 is not shown in FIG. 3 , it is preferably remotely installed and connected to the coupling system 100 by lines.

4 shows a block diagram of a coupling system 100 . The coupling system 100 may be connected to an external control device 405 by the interface 168 . The control device 405 controls in particular the transfer of material by means of a belt conveyor, in particular a process which typically comprises coupling of rotational movements between the input side 110 and the output side 115 of the coupling 105 . a memory-programmable controller (also referred to as a programmable logic controller (PLC)), wherein a drive motor acts as a drive roller of the conveyor belt via the coupling 105 . It is possible in particular for parameters including set values such as rotation speed or torque on the output side 115 to be interchanged via the interface 168 . The control device 166 is preferably designed to control all other operations in the coupling system 100 , here appropriate internal operating parameters, in accordance with specifications. Standardized feedback on operation or error conditions may also be provided via the interface 168 .

The control device 166 is preferably designed to operate the pumping device 164 as explicitly described above. Also, the fan 172 may be operated by the control device 166 according to operating parameters of the coupling system 100 . Operating parameters taken from the coupling 105 are the rotational speed of the rotational speed sensor 222 , the fluid level of the level switch 208 , the fluid temperature of the temperature sensor 192 or the sensor of the filter 188 . may include a blockage signal of Other signals or other sensors are possible.

5 shows a flow diagram of a method 500 for controlling the coupling 105 of the coupling system 100 . The method 500 may in particular be performed on a processing device at least partially on or included in the control device 166 .

In step 505 , parameters may be received via the interface 168 . In step 510 , parameters of the coupling 105 may be determined. Steps 505 and 510 may be executed concurrently for the remainder of the steps, but generally affect other executions.

In step 515, the operation mode may be determined or determined based on the sensed parameters. A first mode of operation 520 relates to the filling of the coupling 105 with a fluid 140 . To this end, the pumping device 164 is operated to deliver a high volumetric flow rate in the first delivery direction described above.

A second mode of operation 525 is associated with maintaining a constant amount of fluid 140 contained within the working space 135 of the coupling 105 . To this end, the pumping device 164 is preferably operated to deliver a low volumetric flow rate in the first delivery direction.

In a third mode of operation 530 , the fluid 140 is evacuated from the working space 135 of the coupling 105 . To this end, the pumping device 164 is preferably operated to deliver in a second delivery direction. Here, the volumetric flow rate is usually as high as possible.

A fourth mode of operation 535 is associated with the pulse operation. This mode of operation is preferably used to support extended phases of operation of the coupling 105 with slip within an area of about 100%. Here, the pumping device 164 is alternately opened in the first and second delivery directions. The duty cycle and period duration of the pulsed operation may be applied to the coupling 105 of the present invention.

A fifth mode of operation 540 relates to static cooling. Here, the fluid 140 is cooled while the coupling 105 itself is stopped. Referring to FIG. 2 , for this purpose, at the same time the valve 216 is opened to discharge the fluid 140 exiting the heat exchanger 170 directly into the tank 160 , in particular the pumping device 164 . It is possible that is operable to deliver in the first delivery direction.

In the sixth operation mode 545 , the heat exchanger 170 may be preheated. This can be convenient at very low outside temperatures, especially below about -20°C. Referring to the embodiment of FIG. 1 , the pumping device 164 transfers a fluid 140 to the outside of the tank 160 through the heat exchanger 170 between the outlet 152 and the inlet 156 . operable to deliver in said first delivery direction to counter normal flow. Here, the fluid flow is preferably between the high and low fluid flow in terms of quantity.

It is noted that the illustrated modes of operation 520 - 545 are exemplary only, and that other or additional modes of operation may be implemented in other embodiments. In addition, the described modes may also be changed in terms of content.

100: coupling system 105: fill-controlled hydrodynamic coupling

110: input side 115: output side

120: axis of rotation 125: pump wheel

130: turbine wheel 135: work space

140: fluid 145: bearing

150: lubrication line 152: outlet

154: direct circulation 156: inlet

158: another outlet 160: tank (fluid source)

162: hydraulic system 164: pumping device

166: control unit 168: interface

170: heat exchanger 172: fan

174: bypass valve 176: orifice plate

178: check valve 180: bypass valve

182: bypass valve 184: orifice plate

186: check valve 188: filter

190: bypass valve 192: temperature sensor

194: pressure sensor 202: housing

204: exhaust means 206: heating device

208: level switch 210: inspection glass

212: orifice plate 214: orifice plate

216: valve 218: bypass valve

220: torque sensor 222: rotational speed sensor

405: external control device 500: method

505: detection of parameters 510: determination of parameters

515: Determination of operation mode 520: Charging (first operation mode)

525: keep constant (second operation mode)

530: empty (third operation mode) 535: pulsing (fourth operation mode)

540: static cooling (fifth operation mode)

545: heat exchanger preheat (sixth operation mode)

Claims (16)

delete delete delete delete delete delete delete delete delete delete delete A method (500) for controlling a fill-controlled hydrodynamic coupling (105), the coupling (105) comprising:
a pump wheel 125 and a turbine wheel 130 defining a working space 135 and capable of being mechanically connected to each other by a hydraulic fluid 140 ;
a direct circulation (154) connecting the hydraulic outlet (152) of the working space (135) to the hydraulic inlet (156) of the working space (135);
a pumping device (164) hydraulically disposed between the fluid source (160) and the direct circulation (154); and
a lubrication line (150) connected from the pumping device (164) to a lubrication point (145) of the coupling (105);
The method 500,
operating (520, 525) the pumping device (164) in a first delivery direction to supply the fluid (140) to the lubrication point (145) and the working space (135); and
operating (530) the pumping device (164) in a second delivery direction to reduce the amount of the fluid (140) received within the working space (135);
The pumping device 164 may be accommodated within the working space 135 or at a relatively high volumetric flow rate in the first delivery direction to increase the amount of the fluid 140 received within the working space 135 . The method (500) of any one of the preceding claims, wherein the method (500) is operated (520) at a relatively low volumetric flow rate (530) to keep the amount of the fluid (140) constant. delete 13. The system of claim 12, wherein the pumping device (164) supplies a fluid (140) to the lubrication point (145) while the slip between the pump wheel (125) and the turbine wheel (130) is 100%. and operating in a pulsed manner (535) in said first delivery direction to 13. Method (500) according to claim 12, characterized in that the fluid is delivered in the first delivery direction through a heat exchanger for stationary to stationary cooling to the pump wheel (125). 13. A computer program product comprising program code means for performing the method (500) according to claim 12 when the computer program product is executed on a processing device (166) or stored on a computer readable data carrier.

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